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EP1469235A1 - Hydraulic control and regulating system and method for adjusting the hydraulic pressure levels - Google Patents

Hydraulic control and regulating system and method for adjusting the hydraulic pressure levels Download PDF

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Publication number
EP1469235A1
EP1469235A1 EP03008967A EP03008967A EP1469235A1 EP 1469235 A1 EP1469235 A1 EP 1469235A1 EP 03008967 A EP03008967 A EP 03008967A EP 03008967 A EP03008967 A EP 03008967A EP 1469235 A1 EP1469235 A1 EP 1469235A1
Authority
EP
European Patent Office
Prior art keywords
pressure circuit
hydraulic fluid
hydraulic
high pressure
circuit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP03008967A
Other languages
German (de)
French (fr)
Inventor
Günter Ebinger
Matthias Burmeister
Eric Sandstorm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BorgWarner Inc filed Critical BorgWarner Inc
Priority to EP03008967A priority Critical patent/EP1469235A1/en
Publication of EP1469235A1 publication Critical patent/EP1469235A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing

Definitions

  • the invention relates to a hydraulic control and regulating system according to the preamble of claim 1 and a method for setting hydraulic pressure levels according to the generic term of claim 7.
  • a hydraulic Control system which is different Hydraulic fluid circuits with different Maintains pressure levels.
  • a first circle the high pressure circle, actuates the clutches and other actuators and must therefore have a relatively high pressure level.
  • the second Circuit the low pressure circuit takes on lubrication and cooling tasks at relatively low pressures but with a high volume flow requirement. To make this cheap in terms of efficiency To implement is the use of a hydraulic pump per circuit meaningful.
  • a first main pressure regulator for the high pressure circuit and a second main pressure regulator for the low pressure circuit provided.
  • the object of the invention therefore arises in a hydraulic Introduce control system, in which the Delivery volume of the individual pump stages is relatively small can be held. Furthermore, it is an object of the invention to provide a method for adjusting hydraulic pressure levels, which compared to conventional methods - one has improved efficiency.
  • This task is carried out by a hydraulic control system with the features of claim 1 and by a Procedure for setting hydraulic pressure levels with solved the features of claim 7 according to the invention.
  • the invention is based on a hydraulic control and regulating system in a manner known per se, with one of a first Hydraulic pump with high pressure circuit fed with hydraulic fluid, whose high pressure level can be regulated by a first main pressure regulator and with one of a second hydraulic pump with hydraulic fluid fed low pressure circuit, its low pressure level can be regulated by a second main pressure regulator.
  • the invention is based on the idea of the invention, high and Network low pressure circuit with each other.
  • the invention there is therefore a hydraulic fluid drain in the high pressure circuit provided through which the low pressure circuit with excess hydraulic fluid from the high pressure circuit is feedable.
  • the invention provides an alternative to this or in addition a hydraulic fluid inlet in the high pressure circuit over which the high pressure circuit with missing hydraulic fluid can be fed by the second hydraulic pump.
  • the excess hydraulic fluid in the high pressure circuit preferably by the first main pressure regulator limited and can now be used in the low pressure circuit, because it still contains usable energy.
  • the hydraulic pump of the low pressure circuit can be connected to the high pressure circuit. This is particularly in the case of the automatic transmission described above (e.g. dual clutch transmission) for filling the Couplings with hydraulic fluid make sense.
  • the hydraulic fluid drain and / or the hydraulic fluid inlet components of the first main pressure regulator are basically not necessary.
  • the first main pressure regulator by means of one provided in the high pressure circuit Valve controlled depending on the pressure in the high pressure circuit becomes.
  • a conventional solenoid valve comes here to be used, which has a flow orifice the high pressure circuit is connected. Because such a solenoid valve usually to control the first anyway Main pressure regulator used are only minor modifications necessary to a hydraulic control system to provide in the manner according to the invention.
  • the second hydraulic pump intermediate pressure circuit supplied with hydraulic fluid is provided, through which the low pressure circuit with the hydraulic fluid is feedable. Simultaneously or alternatively, the High pressure circuit via this intermediate pressure circuit with the missing one Hydraulic fluid can be fed.
  • Such an intermediate pressure circuit ensures that fluctuations in one of the Main pressure circuits (high and low pressure circuit) none or only have a minor impact on the other main pressure circuit.
  • a pressure relief valve is provided through which the low pressure circuit with excess hydraulic fluid from the intermediate pressure circuit is food-saving. This additional amount of hydraulic fluid can easily from the second main pressure regulator be curtailed.
  • the hydraulic control system shown in FIG. 1 1 is based on two pressure circuits, a high pressure circuit 2 with the help of its couplings and / or other actuators 2.1 are operated, and a low-pressure circuit 3, which Lubrication and cooling tasks 2.2 at relatively low pressures but with a high volume flow requirement.
  • the high-pressure circuit 2 is fed by a first hydraulic pump 4, which draws hydraulic fluid filtered by a filter 10 from a hydraulic fluid reservoir 16 via a supply circuit 12.
  • the pressure level P A in this high-pressure circuit 2 is regulated as a rule from the pressure P 4 provided by the hydraulic pump 4 with the aid of the first main pressure regulator 6.
  • the low-pressure circuit 3 is essentially fed by a second hydraulic pump 5, which also removes the hydraulic fluid filtered by the filter 10 via the supply circuit 12 from the hydraulic fluid reservoir 16.
  • the provided from said second hydraulic pump 5 is regulated pressure P 5 by means of a second main pressure regulator 7 to the low pressure level P L as a rule.
  • the second main pressure regulator 7 of the low pressure circuit 3 is in performed in a known manner. So that includes hydraulically actuatable second main pressure regulator 7 in the present embodiment an essentially cylindrical control housing, which has eight slots over its axial extent (or bags) 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 having.
  • a piston 7.1 in the axial direction guided to a limited extent.
  • the first end face 7.2 of the Piston 7.1 forms a one-sided stop on one end side of the control housing.
  • a piston actuating spring 7.4 is arranged, which the first face (in the absence of any other force the piston 7.1) pressed against one end side of the control housing holds.
  • the piston 7.1 has different along its axial extent Diameter on. There are four piston sections 7.8, 7.9, 7.10, 7.11, which are essentially form-fitting in the inner wall of the control housing, and three Piston sections 7.5, 7.6, 7.7, which have a smaller outer diameter exhibit. A piston section 7.5, 7.6, 7.7 of the latter type is in the axial direction between each two piston sections 7.8, 7.9, 7.10, 7.11 of the former Sort arranged.
  • Hydraulic fluid cannot flow out of the low pressure circuit 3 via the second main pressure regulator 7. If the pressure P L in the low-pressure circuit 3 exceeds this predeterminable threshold value, the hydraulic fluid passed via the slot 7.12 to the end face 7.2 of the piston 7.1 will push the piston 7.1 to the right against the force of the piston actuating spring 7.4. This enables hydraulic fluid to flow from slot 7.13 to slot 7.14, from slot 7.15 to slot 7.16 and, at particularly high pressures P L , from slot 7.17 to slot 7.18. Hydraulic fluid can therefore on the one hand reach the first hydraulic pump via the filter 11, the cooler 15 and, in the case of particularly high pressures P L , the second hydraulic pump 5.
  • the first main pressure regulator 6 is like in the present example executed as follows:
  • It comprises an essentially cylindrical control housing, which has 8 slots 6.10, 6.11, 6.12, 6.13, 6.14, 6.15, 6.16, 6.17.
  • a piston 6.1 in the axial direction guided to a limited extent.
  • the two end faces 6.2, 6.3 of the piston 6.1 form end stops on the respective End faces of the control housing.
  • a piston actuation spring 6.4 is in the control housing of the first main pressure regulator 6 used that the first end face 6.2 with negligible other force acting on the piston 6.1 against one end of the control housing is held down.
  • the piston 6.1 has similar to the second main pressure regulator 7 different diameters along its axial extent on. There are two opening piston sections 6.5, 6.6 and three closing piston sections 6.7, 6.8 and 6.9.
  • the piston 6.1 of the first main pressure regulator 6 against the actuating force of the piston actuating spring 6.4 be brought into any intermediate position.
  • the piston 6.1 is at the right stop. A hydraulic fluid flow from high pressure circuit 2 to low pressure circuit 3 is not possible. Furthermore, no flow from the intermediate pressure circuit 13 to the low pressure circuit 3 is possible. However, there is a flow connection from the intermediate pressure circuit 13 via the slot 6.12 to the slot 6.13 in the high pressure circuit 2. In this piston position, both the first hydraulic pump 4 and the second hydraulic pump 5 feed the high pressure circuit 2 due to its high volume flow requirement.
  • the piston 6.1 At medium pressure conditions P A in the high pressure circuit 2, the piston 6.1 is in the position shown in FIG. 1. In this case, the high-pressure circuit 2 is fed exclusively by the first hydraulic pump 4. The low pressure circuit 3 is fed exclusively via the intermediate pressure circuit 13 and the slots 6.12 and 6.11 by the second hydraulic pump 5.
  • the invention provides a pressure relief valve 9 which opens when a predefinable threshold value is exceeded and releases a flow from the intermediate pressure circuit 13 to the low pressure circuit 3.
  • the solenoid valve 8 is used for hydraulic pilot control of the first main pressure regulator 6. With the solenoid valve 8, a current-proportional pressure signal, the so-called pilot pressure P A ', can be generated. The current is specified by a central electronic transmission control unit (not shown). The orifice 14 in the supply line 2 'to the solenoid valve 8 limits the incoming volume flow to the value P A '.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Transmission Device (AREA)

Abstract

The system (1) has a high-pressure circuit (2) supplied by a first hydraulic pump (4) with a first main pressure regulator (6) and a low pressure circuit (3) supplied by a second pump (5) with a second main pressure regulator (7). The high-pressure circuit has a hydraulic fluid outlet (6.14,6.6,6.15) via which the low pressure circuit is supplied with excess fluid and/or a hydraulic inlet (6.12,6.5,6.13) via which the high-pressure circuit is supplied with missing fluid by the second pump. An independent claim is also included for a method of adjusting a hydraulic pressure level.

Description

Die Erfindung betrifft ein hydraulisches Steuer- und Regelsystem gemäß dem Oberbegriff des Anspruchs 1 sowie ein Verfahren zum Einstellen von hydraulischen Druckniveaus nach dem Oberbegriff des Patentanspruchs 7.The invention relates to a hydraulic control and regulating system according to the preamble of claim 1 and a method for setting hydraulic pressure levels according to the generic term of claim 7.

Insbesondere bei Kraftfahrzeugen ist es üblich, dass ein hydraulisches Steuer- und Regelsystem vorhanden ist, welches unterschiedliche Hydraulikflüssigkeitskreise mit unterschiedlichen Druckniveaus unterhält. Zum Betrieb eines Automatikgetriebes, insbesondere eines Doppelkupplungsgetriebes, ist es insbesondere sinnvoll, zwei unterschiedliche Hydraulikflüssigkeitskreisläufe vorzusehen. Ein erster Kreis, der Hochdruckkreis, betätigt die Kupplungen und andere Aktuatoren und muss deshalb über ein relativ hohes Druckniveau verfügen. Der zweite Kreis, der Niederdruckkreis übernimmt Schmier- und Kühlaufgaben bei relativ niedrigen Drücken aber mit einem hohen Volumenstrombedarf. Um dies hinsichtlich des Wirkungsgrades günstig umzusetzen, ist die Verwendung einer Hydropumpe je Kreislauf sinnvoll. Dabei ist gemäß dem betriebsinternen Stand der Technik bekannt, einen ersten Hauptdruckregler für den Hochdruckkreis und einen zweiten Hauptdruckregler für den Niederdruckkreis vorzusehen.In motor vehicles in particular, it is common for a hydraulic Control system is available, which is different Hydraulic fluid circuits with different Maintains pressure levels. To operate an automatic transmission, in particular a double clutch transmission, it is particularly useful, two different hydraulic fluid circuits provided. A first circle, the high pressure circle, actuates the clutches and other actuators and must therefore have a relatively high pressure level. The second Circuit, the low pressure circuit takes on lubrication and cooling tasks at relatively low pressures but with a high volume flow requirement. To make this cheap in terms of efficiency To implement is the use of a hydraulic pump per circuit meaningful. According to the internal status of the company Known technology, a first main pressure regulator for the high pressure circuit and a second main pressure regulator for the low pressure circuit provided.

Obwohl sich ein derartiges hydraulisches Steuer- und Regelsystem dem Grunde nach bewährt hat, entsteht weiterhin das Bedürfnis den Wirkungsgrad zu verbessern. Although such a hydraulic control and regulation system has basically proven itself, the need continues to arise improve efficiency.

Die Aufgabe der Erfindung entsteht demzufolge darin, ein hydraulisches Steuer- und Regelsystem vorzustellen, bei dem das Fördervolumen der einzelnen Pumpenstufen verhältnismäßig klein gehalten werden kann. Weiterhin ist es Aufgabe der Erfindung, ein Verfahren zum Einstellen hydraulischer Druckniveaus bereitzustellen, welches gegenüber herkömmlichen Verfahren-einen verbesserten Wirkungsgrad aufweist.The object of the invention therefore arises in a hydraulic Introduce control system, in which the Delivery volume of the individual pump stages is relatively small can be held. Furthermore, it is an object of the invention to provide a method for adjusting hydraulic pressure levels, which compared to conventional methods - one has improved efficiency.

Diese Aufgabe wird durch ein hydraulisches Steuer- und Regelsystem mit den Merkmalen des Patentanspruchs 1 sowie durch ein Verfahren zum Einstellen von hydraulischen Druckniveaus mit den Merkmalen des Patentanspruchs 7 erfindungsgemäß gelöst.This task is carried out by a hydraulic control system with the features of claim 1 and by a Procedure for setting hydraulic pressure levels with solved the features of claim 7 according to the invention.

Vorteilhafte Ausführungen und Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.Advantageous embodiments and developments of the invention are specified in the subclaims.

Die Erfindung geht von einem hydraulischen Steuer- und Regelsystem an sich bekannter Art aus, mit einem von einer ersten Hydropumpe mit Hydraulikflüssigkeit gespeisten Hochdruckkreis, dessen Hochdruckniveau von einem ersten Hauptdruckregler regelbar ist und mit einem von einer zweiten Hydropumpe mit Hydraulikflüssigkeit gespeisten Niederdruckkreis, dessen Niederdruckniveau von einem zweiten Hauptdruckregler regelbar ist.The invention is based on a hydraulic control and regulating system in a manner known per se, with one of a first Hydraulic pump with high pressure circuit fed with hydraulic fluid, whose high pressure level can be regulated by a first main pressure regulator and with one of a second hydraulic pump with hydraulic fluid fed low pressure circuit, its low pressure level can be regulated by a second main pressure regulator.

Der Erfindung liegt der Erfindungsgedanke zu Grunde, Hoch- und Niederdruckkreis miteinander zu vernetzen.The invention is based on the idea of the invention, high and Network low pressure circuit with each other.

Erfindungsgemäß ist daher in dem Hochdruckkreis ein Hydraulikflüssigkeitsablass vorgesehen, über den der Niederdruckkreis mit überschüssiger Hydraulikflüssigkeit aus dem Hochdruckkreis speisbar ist. Alternativ hierzu oder zusätzlich sieht die Erfindung in dem Hochdruckkreis einen Hydraulikflüssigkeitseinlass vor über den der Hochdruckkreis mit fehlender Hydraulikflüssigkeit von der zweiten Hydropumpe speisbar ist.According to the invention there is therefore a hydraulic fluid drain in the high pressure circuit provided through which the low pressure circuit with excess hydraulic fluid from the high pressure circuit is feedable. The invention provides an alternative to this or in addition a hydraulic fluid inlet in the high pressure circuit over which the high pressure circuit with missing hydraulic fluid can be fed by the second hydraulic pump.

Einerseits wird also die im Hochdruckkreis überschüssige Hydraulikflüssigkeit vorzugsweise durch den ersten Hauptdruckregler abgeregelt und kann nun im Niederdruckkreis verwendet werden, da es noch nutzbare Energie enthält. Andererseits ist erfindungsgemäß ebenfalls vorgesehen, dass bei hohem Volumenstrombedarf im Hochdruckkreis die Hydropumpe des Niederdruckkreises zum Hochdruckkreis dazugeschaltet werden kann. Dies ist insbesondere im Fall des vorstehend beschriebenen Automatikgetriebes (z. B. Doppelkupplungsgetriebe) zum Füllen der Kupplungen mit Hydraulikmittel sinnvoll. Durch die Vernetzung der beiden Kreisläufe (Hochdruckkreis und Niederdruckkreis) in der vorbeschriebenen Weise kann das Fördervolumen der einzelnen Pumpenstufen verhältnismäßig klein gehalten werden.On the one hand, the excess hydraulic fluid in the high pressure circuit preferably by the first main pressure regulator limited and can now be used in the low pressure circuit, because it still contains usable energy. On the other hand, is according to the invention also provided that with high volume flow requirements in the high pressure circuit the hydraulic pump of the low pressure circuit can be connected to the high pressure circuit. This is particularly in the case of the automatic transmission described above (e.g. dual clutch transmission) for filling the Couplings with hydraulic fluid make sense. Through networking of the two circuits (high pressure circuit and low pressure circuit) in In the manner described above, the funding volume of each Pump stages are kept relatively small.

Wie bereits vorstehend angedeutet wurde, ist es erfindungsgemäß vorgesehen, dass der Hydraulikflüssigkeitsablass und/oder der Hydraulikflüssigkeitseinlass Bestandteile des ersten Hauptdruckreglers sind. Zusätzliche Regelkomponenten sind also grundsätzlich nicht erforderlich.As already indicated above, it is according to the invention provided that the hydraulic fluid drain and / or the hydraulic fluid inlet components of the first main pressure regulator. Additional control components are basically not necessary.

Erfindungsgemäß ist ferner vorgesehen, dass der erste Hauptdruckregler mittels eines in dem Hochdruckkreis vorgesehenen Ventils in Abhängigkeit vom Druck im Hochdruckkreis gesteuert wird. Üblicherweise kommt hier ein herkömmliches Elektromagnetventil zum Einsatz, welches über eine Druchflussblende an den Hochdruckkreis angeschlossen ist. Da ein derartiges Elektromagnetventil üblicherweise ohnehin zur Steuerung des ersten Hauptdruckreglers verwendet wird, sind nur geringfügige Modifikationen notwendig, um ein hydraulisches Steuer- und Regelsystem in der erfindungsgemäßen Art bereitzustellen. According to the invention it is further provided that the first main pressure regulator by means of one provided in the high pressure circuit Valve controlled depending on the pressure in the high pressure circuit becomes. Usually a conventional solenoid valve comes here to be used, which has a flow orifice the high pressure circuit is connected. Because such a solenoid valve usually to control the first anyway Main pressure regulator used are only minor modifications necessary to a hydraulic control system to provide in the manner according to the invention.

Erfindungsgemäß ist weiterhin ein von der zweiten Hydropumpe mit Hydraulikflüssigkeit gespeister Zwischendruckkreis vorgesehen, über den der Niederdruckkreis mit der Hydraulikflüssigkeit speisbar ist. Gleichzeitig oder alternativ hierzu ist der Hochdruckkreis über diesen Zwischendruckkreis mit der fehlenden Hydraulikflüssigkeit speisbar. Ein derartiger Zwischendruckkreis stellt sicher, dass Schwankungen in einem der Hauptdruckkreise (Hoch- und Niederdruckkreis) keine oder nur geringfügige Auswirkungen auf den anderen Hauptdruckkreis haben.According to the invention is also one of the second hydraulic pump intermediate pressure circuit supplied with hydraulic fluid is provided, through which the low pressure circuit with the hydraulic fluid is feedable. Simultaneously or alternatively, the High pressure circuit via this intermediate pressure circuit with the missing one Hydraulic fluid can be fed. Such an intermediate pressure circuit ensures that fluctuations in one of the Main pressure circuits (high and low pressure circuit) none or only have a minor impact on the other main pressure circuit.

In einer besonderen Ausgestaltung dieser Variante ist vorgesehen, dass die Speisung des Niederdruckkreises mit der Hydraulikflüssigkeit aus dem Zwischendruckkreis und/oder die Speisung des Hochdruckkreises mit der fehlenden Hydraulikflüssigkeit aus dem Zwischendruckkreis von dem ersten Hauptdruckregler regelbar ist. Es brauchen folglich keine zusätzlichen Ventile vorgesehen werden, die diese Aufgabe übernehmen, sondern es reicht die entsprechende Ausgestaltung des ersten Hauptdruckreglers.In a special embodiment of this variant, that the supply of the low pressure circuit with the hydraulic fluid from the intermediate pressure circuit and / or the feed the high pressure circuit with the missing hydraulic fluid from the intermediate pressure circuit from the first main pressure regulator is adjustable. As a result, no additional valves are required are provided that take on this task, but the corresponding design of the first main pressure regulator is sufficient.

Für den Fall, dass in dem Zwischendruckkreis ein Überdruck herrscht, beispielsweise weil aus dem Zwischendruckkreis nur eine geringe Menge Hydraulikflüssigkeit in den Hochdruckkreis abgegeben wird, ist erfindungsgemäß in dem Zwischendruckkreis ein Überdruckventil vorgesehen, über das der Niederdruckkreis mit überschüssiger Hydraulikflüssigkeit aus dem Zwischendruckkreis speispar ist. Diese zusätzliche Hydraulikflüssigkeitsmenge kann in einfacher Weise von dem zweiten Hauptdruckregler abgeregelt werden. In the event that there is an overpressure in the intermediate pressure circuit prevails, for example because only from the intermediate pressure circle a small amount of hydraulic fluid in the high pressure circuit is released, is according to the invention in the intermediate pressure circle a pressure relief valve is provided through which the low pressure circuit with excess hydraulic fluid from the intermediate pressure circuit is food-saving. This additional amount of hydraulic fluid can easily from the second main pressure regulator be curtailed.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt. Es zeigen:

Figur 1
ein Prinzipschaltbild eines erfindungsgemäßen hydraulischen Steuer- und Regelsystems, wie es beispielsweise zur hydraulischen Steuerung eines Doppelkupplungsgetriebes eingesetzt wird.
An embodiment of the invention is shown in the drawing. Show it:
Figure 1
a schematic diagram of a hydraulic control and regulating system according to the invention, as it is used for example for the hydraulic control of a double clutch transmission.

Das in der Figur 1 dargestellte hydraulische Steuer- und Regelsystem 1 basiert auf zwei Druckkreisen, einem Hochdruckkreis 2 mit Hilfe dessen Kupplungen und/oder sonstige Aktuatoren 2.1 betätigt werden, sowie einem Niederdruckkreis 3, welcher Schmier- und Kühlaufgaben 2.2 bei relativ niedrigen Drücken aber mit einem hohen Volumenstrombedarf übernimmt.The hydraulic control system shown in FIG. 1 1 is based on two pressure circuits, a high pressure circuit 2 with the help of its couplings and / or other actuators 2.1 are operated, and a low-pressure circuit 3, which Lubrication and cooling tasks 2.2 at relatively low pressures but with a high volume flow requirement.

Der Hochdruckkreis 2 wird von einer ersten Hydropumpe 4 gespeist, welche von einem Filter 10 gefilterte Hydraulikflüssigkeit über einen Versorgungskreis 12 aus einem Hydraulikflüssigkeitsreservoir 16 entnimmt. Das Druckniveau PA in diesem Hochdruckkreis 2 wird im Regelfall aus dem von der Hydropumpe 4 bereitgestellten Druck P4 mit Hilfe des ersten Hauptdruckreglers 6 abgeregelt.The high-pressure circuit 2 is fed by a first hydraulic pump 4, which draws hydraulic fluid filtered by a filter 10 from a hydraulic fluid reservoir 16 via a supply circuit 12. The pressure level P A in this high-pressure circuit 2 is regulated as a rule from the pressure P 4 provided by the hydraulic pump 4 with the aid of the first main pressure regulator 6.

Der Niederdruckkreis 3 wird im wesentlichen von einer zweiten Hydropumpe 5 gespeist, welche die von dem Filter 10 gefilterte Hydraulikflüssigkeit über den Versorgungskreis 12 ebenfalls aus dem Hydraulikflüssigkeitsreservoir 16 entnimmt. Dabei wird im Regelfall der von dieser zweiten Hydropumpe 5 bereitgestellte Druck P5 mit Hilfe eines zweiten Hauptdruckreglers 7 auf das Niederdruckniveau PL abgeregelt.The low-pressure circuit 3 is essentially fed by a second hydraulic pump 5, which also removes the hydraulic fluid filtered by the filter 10 via the supply circuit 12 from the hydraulic fluid reservoir 16. Here, the provided from said second hydraulic pump 5 is regulated pressure P 5 by means of a second main pressure regulator 7 to the low pressure level P L as a rule.

Der zweite Hauptdruckregler 7 des Niederdruckkreises 3 ist in an sich bekannter Art ausgeführt. So umfasst der hydraulisch betätigbare zweite Hauptdruckregler 7 im vorliegenden Ausführungsbeispiel ein im wesentlichen zylinderförmiges Steuergehäuse, welches über dessen axialer Erstreckung acht Schlitze (oder Taschen) 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 aufweist.The second main pressure regulator 7 of the low pressure circuit 3 is in performed in a known manner. So that includes hydraulically actuatable second main pressure regulator 7 in the present embodiment an essentially cylindrical control housing, which has eight slots over its axial extent (or bags) 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 having.

In diesem Steuergehäuse ist in axialer Richtung ein Kolben 7.1 begrenzt verschieblich geführt. Die erste Stirnseite 7.2 des Kolbens 7.1 bildet einen einendseitigen Anschlag an einer Endseite des Steuergehäuses. Zwischen der zweiten Stirnseite 7.3 des Kolbens 7.1 und der anderen Endseite des Steuergehäuses ist eine Kolbenbetätigungsfeder 7.4 angeordnet, welche die erste Stirnseite (bei fehlender sonstiger Krafteinwirkung auf den Kolben 7.1) gegen die eine Endseite des Steuergehäuses gedrückt hält.In this control housing there is a piston 7.1 in the axial direction guided to a limited extent. The first end face 7.2 of the Piston 7.1 forms a one-sided stop on one end side of the control housing. Between the second end face 7.3 the piston 7.1 and the other end of the control housing a piston actuating spring 7.4 is arranged, which the first face (in the absence of any other force the piston 7.1) pressed against one end side of the control housing holds.

Der Kolben 7.1 weist längs seiner axialen Erstreckung unterschiedliche Durchmesser auf. Es gibt vier Kolbenabschnitte 7.8, 7.9, 7.10, 7.11, welche im wesentlichen formschlüssig in der Innenwandung des Steuergehäuses geführt sind, sowie drei Kolbenabschnitte 7.5, 7.6, 7.7, welche einen kleineren Außendurchmesser aufweisen. Ein Kolbenabschnitt 7.5, 7.6, 7.7 der letztgenannten Art ist dabei in axialer Richtung jeweils zwischen zwei Kolbenabschnitten 7.8, 7.9, 7.10, 7.11 der erstgenannten Art angeordnet.The piston 7.1 has different along its axial extent Diameter on. There are four piston sections 7.8, 7.9, 7.10, 7.11, which are essentially form-fitting in the inner wall of the control housing, and three Piston sections 7.5, 7.6, 7.7, which have a smaller outer diameter exhibit. A piston section 7.5, 7.6, 7.7 of the the latter type is in the axial direction between each two piston sections 7.8, 7.9, 7.10, 7.11 of the former Sort arranged.

Erstreckt sich ein Kolbenabschnitt 7.5, 7.6, 7.7 der letztgenannten Art in einer bestimmten Stellung des Kolbens 7.1 in dem Steuergehäuse von einem Schlitz 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 zu einem benachbarten Schlitz 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19, so ist ein Hydraulikflüssigkeitsdurchfluss zwischen diesen beiden benachbarten Schlitzen 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 möglich. Ein Kolbenabschnitt 7.5, 7.6, 7.7 der letztgenannten Art wird daher im Folgenden als öffnender Kolbenabschnitt 7.5, 7.6, 7.7 bezeichnet. Die anderen formschlüssig an der Innenwandung des Steuergehäuses geführten Kolbenabschnitte 7.8, 7.9, 7.10, 7.11 werden nachfolgend als schließende Kolbenabschnitte 7.8, 7.9, 7.10 und 7.11 bezeichnet, da hier kein Durchfluss von Hydraulikflüssigkeit zwischen benachbarten Schlitzen 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 möglich ist.Extends a piston section 7.5, 7.6, 7.7 of the latter Kind in a certain position of the piston 7.1 in the control housing from a slot 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 to an adjacent slot 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19, this is a hydraulic fluid flow between these two neighboring ones Slots 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 possible. A piston section 7.5, 7.6, 7.7 of the latter type is therefore referred to below as the opening piston section 7.5, 7.6, 7.7 referred. The other form-fitting on the inner wall piston sections 7.8 of the control housing, 7.9, 7.10, 7.11 are hereinafter referred to as closing piston sections 7.8, 7.9, 7.10 and 7.11, since none here Flow of hydraulic fluid between adjacent ones Slots 7.12, 7.13, 7.14, 7.15, 7.16, 7.17, 7.18, 7.19 possible is.

Ist der Druck PL im Niederdruckkreis 3 kleiner als ein vorgebbarer Schwellwert, so befindet sich der Kolben 7.1 in der in der Figur 1 dargestellten Position. Hydraulikflüssigkeit kann aus dem Niederdruckkreis 3 über den zweiten Hauptdruckregler 7 nicht abfließen. Übersteigt der Druck PL im Niederdruckkreis 3 diesen vorgebbaren Schwellwert, so wird die über den Schlitz 7.12 auf die Stirnseite 7.2 des Kolbens 7.1 geleitete Hydraulikflüssigkeit den Kolben 7.1 entgegen der Kraft der Kolbenbetätigungsfeder 7.4 nach rechts drücken. Dadurch ist ein Hydraulikflüssigkeitsdurchfluss vom Schlitz 7.13 zum Schlitz 7.14, vom Schlitz 7.15 zum Schlitz 7.16 sowie bei besonders hohen Drücken PL auch vom Schlitz 7.17 zum Schlitz 7.18 möglich. Hydraulikflüssigkeit kann daher zum einen über den Filter 11 zur ersten Hydropumpe, zum Kühler 15 sowie bei besonders hohen Drücken PL wiederum zur zweiten Hydropumpe 5 gelangen.If the pressure P L in the low-pressure circuit 3 is less than a predeterminable threshold value, the piston 7.1 is in the position shown in FIG. 1. Hydraulic fluid cannot flow out of the low pressure circuit 3 via the second main pressure regulator 7. If the pressure P L in the low-pressure circuit 3 exceeds this predeterminable threshold value, the hydraulic fluid passed via the slot 7.12 to the end face 7.2 of the piston 7.1 will push the piston 7.1 to the right against the force of the piston actuating spring 7.4. This enables hydraulic fluid to flow from slot 7.13 to slot 7.14, from slot 7.15 to slot 7.16 and, at particularly high pressures P L , from slot 7.17 to slot 7.18. Hydraulic fluid can therefore on the one hand reach the first hydraulic pump via the filter 11, the cooler 15 and, in the case of particularly high pressures P L , the second hydraulic pump 5.

Der erste Hauptdruckregler 6 ist im vorliegenden Beispiel wie folgt ausgeführt:The first main pressure regulator 6 is like in the present example executed as follows:

Er umfasst ein im wesentlichen zylinderförmiges Steuergehäuse, welches über dessen axialer Erstreckung 8 Schlitze 6.10, 6.11, 6.12, 6.13, 6.14, 6.15, 6.16, 6.17 aufweist. It comprises an essentially cylindrical control housing, which has 8 slots 6.10, 6.11, 6.12, 6.13, 6.14, 6.15, 6.16, 6.17.

In dem Steuergehäuse ist in axialer Richtung ein Kolben 6.1 begrenzt verschieblich geführt. Die beiden Stirnseiten 6.2, 6.3 des Kolbens 6.1 bilden endseitige Anschläge an den jeweiligen Endseiten des Steuergehäuses. Eine Kolbenbetätigungsfeder 6.4 ist so in das Steuergehäuse des ersten Hauptdruckreglers 6 eingesetzt, dass die erste Stirnseite 6.2 bei vernachlässigbarer sonstiger Krafteinwirkung auf den Kolben 6.1 gegen die eine Endseite des Steuergehäuses gedrückt gehalten wird.In the control housing there is a piston 6.1 in the axial direction guided to a limited extent. The two end faces 6.2, 6.3 of the piston 6.1 form end stops on the respective End faces of the control housing. A piston actuation spring 6.4 is in the control housing of the first main pressure regulator 6 used that the first end face 6.2 with negligible other force acting on the piston 6.1 against one end of the control housing is held down.

Der Kolben 6.1 weist ähnlich dem zweiten Hauptdruckregler 7 längs seiner axialen Erstreckung unterschiedliche Durchmesser auf. Es gibt zwei öffnende Kolbenabschnitte 6.5, 6.6 sowie drei schließende Kolbenabschnitte 6.7, 6.8 und 6.9.The piston 6.1 has similar to the second main pressure regulator 7 different diameters along its axial extent on. There are two opening piston sections 6.5, 6.6 and three closing piston sections 6.7, 6.8 and 6.9.

Entsprechend dem vorgehend beschriebenen zweiten Hauptdruckregler 7 kann der Kolben 6.1 des ersten Hauptdruckreglers 6 entgegen der Betätigungskraft der Kolbenbetätigungsfeder 6.4 in eine beliebige Zwischenstellung verbracht werden. Erstreckt sich ein öffnender Kolbenabschnitt 6.5 oder 6.6 in einer bestimmten Stellung des Kolbens 6.1 in dem Steuergehäuse von einem Schlitz 6.11, 6.12, 6.13, 6.14, 6.15 zu einem benachbarten Schlitz 6.11, 6.12, 6.13, 6.14, 6.15, so ist wie vorhin ein Hydraulikflüssigkeitsdurchfluss zwischen diesen beiden benachbarten Schlitzen 6.11, 6.12, 6.13, 6.14, 6.15 möglich.Corresponding to the second main pressure regulator described above 7, the piston 6.1 of the first main pressure regulator 6 against the actuating force of the piston actuating spring 6.4 be brought into any intermediate position. extends an opening piston section 6.5 or 6.6 in a certain Position of the piston 6.1 in the control housing of one Slot 6.11, 6.12, 6.13, 6.14, 6.15 to an adjacent one Slot 6.11, 6.12, 6.13, 6.14, 6.15, is as before Hydraulic fluid flow between these two neighboring ones Slots 6.11, 6.12, 6.13, 6.14, 6.15 possible.

Ist der Druck PA niedriger als ein vorgebbarer Schwellwert, so befindet sich der Kolben 6.1 am rechten Anschlag. Ein Hydraulikflüssigkeitsdurchfluss vom Hochdruckkreis 2 zum Niederdruckkreis 3 ist nicht möglich. Weiterhin ist auch kein Durchfluss vom Zwischendruckkreis 13 zum Niederdruckkreis 3 möglich. Jedoch besteht eine Durchflussverbindung vom Zwischendruckkreis 13 über den Schlitz 6.12 zum Schlitz 6.13 in den Hochdruckkreis 2. In dieser Kolbenposition speisen sowohl die erste Hydropumpe 4 als auch die zweite Hydropumpe 5 den Hochdruckkreis 2 aufgrund dessen hohen Volumenstrombedarfs.If the pressure P A is lower than a predefinable threshold value, the piston 6.1 is at the right stop. A hydraulic fluid flow from high pressure circuit 2 to low pressure circuit 3 is not possible. Furthermore, no flow from the intermediate pressure circuit 13 to the low pressure circuit 3 is possible. However, there is a flow connection from the intermediate pressure circuit 13 via the slot 6.12 to the slot 6.13 in the high pressure circuit 2. In this piston position, both the first hydraulic pump 4 and the second hydraulic pump 5 feed the high pressure circuit 2 due to its high volume flow requirement.

Bei mittleren Druckverhältnissen PA im Hochdruckkreis 2 befindet sich der Kolben 6.1 in der in der Figur 1 dargestellten Stellung. In diesem Fall wird der Hochdruckkreis 2 ausschließlich von der ersten Hydropumpe 4 gespeist. Der Niederdruckkreis 3 wird ausschließlich über den Zwischendruckkreis 13 und die Schlitze 6.12 und 6.11 von der zweiten Hydropumpe 5 gespeist.At medium pressure conditions P A in the high pressure circuit 2, the piston 6.1 is in the position shown in FIG. 1. In this case, the high-pressure circuit 2 is fed exclusively by the first hydraulic pump 4. The low pressure circuit 3 is fed exclusively via the intermediate pressure circuit 13 and the slots 6.12 and 6.11 by the second hydraulic pump 5.

Steigt der Druck PA im Hochdruckkreis 2 weiter an, so wird der Kolben 6.1 aufgrund der über den Schlitz 6.17 auf die Stirnseite 6.2 des Kolbens 6.1 wirkenden Hydraulikflüssigkeit weiter nach links geschoben. Die Durchflussverbindung vom Zwischendruckkreis 13 über die Schlitze 6.12 und 6.11 auf den Niederdruckkreis 3 bleibt bestehen. Weiterhin,stellt der öffnende Kolbenabschnitt 6.6 eine Durchflussverbindung zwischen dem Schlitz 6.15 und dem Schlitz 6.14 her. Überschüssige Hydraulikflüssigkeit vom Hochdruckkreis 2 kann über die Schlitze 6.15 und 6.14 in den Niederdruckkreis 3 abfließen.If the pressure P A in the high-pressure circuit 2 continues to rise, the piston 6.1 is pushed further to the left due to the hydraulic fluid acting on the end face 6.2 of the piston 6.1 via the slot 6.17. The flow connection from the intermediate pressure circuit 13 via the slots 6.12 and 6.11 to the low pressure circuit 3 remains. Furthermore, the opening piston section 6.6 establishes a flow connection between the slot 6.15 and the slot 6.14. Excess hydraulic fluid from the high pressure circuit 2 can flow into the low pressure circuit 3 via the slots 6.15 and 6.14.

Befindet sich der Kolben 6.1 in Regelposition, so kann es Betriebspunkte geben, bei denen der Druck P13 im Zwischendruckkreis 13 weiter ansteigen wird, weil die von der zweiten Hydropumpe 5 gelieferte Hydraulikflüssigkeit nicht mehr hinreichend schnell über die Schlitze 6.12 und 6.11 zum Niederdruckkreis 3 abgeführt werden kann. Aus diesem Grund sieht die Erfindung,ein Überdruckventil 9 vor, welches beim Überschreiten eines vorgebbaren Schwellwerts öffnet und einen Durchfluss vom Zwischendruckkreis 13 zum Niederdruckkreis 3 freigibt. If the piston 6.1 is in the control position, there may be operating points at which the pressure P 13 in the intermediate pressure circuit 13 will continue to rise because the hydraulic fluid supplied by the second hydraulic pump 5 is no longer discharged to the low pressure circuit 3 sufficiently quickly via the slots 6.12 and 6.11 can be. For this reason, the invention provides a pressure relief valve 9 which opens when a predefinable threshold value is exceeded and releases a flow from the intermediate pressure circuit 13 to the low pressure circuit 3.

Das Elektromagnetventil 8 dient zur hydraulischen Vorsteuerung des ersten Hauptdruckreglers 6. Mit dem Elektromagnetventil 8 kann ein stromproportionales Drucksignal, der sog. Vorsteuerdruck PA', erzeugt werden. Die Stromvorgabe erfolgt von einem zentralen elektronischen Getriebesteuergerät (nicht gezeichnet). Die Blende 14 in der Versorgungsleitung 2' zum Elektromagnetventil 8 begrenzt den zulaufenden Volumenstrom auf den Wert PA' . The solenoid valve 8 is used for hydraulic pilot control of the first main pressure regulator 6. With the solenoid valve 8, a current-proportional pressure signal, the so-called pilot pressure P A ', can be generated. The current is specified by a central electronic transmission control unit (not shown). The orifice 14 in the supply line 2 'to the solenoid valve 8 limits the incoming volume flow to the value P A '.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
hydraulisches Steuer- und Regelsystemhydraulic control and regulation system
22
HochdruckkreisHigh pressure circuit
2'2 '
Versorgungsleitung im HochdruckkreisSupply line in the high pressure circuit
2.12.1
Aktuatorikactuators
2.22.2
Schmierung / KühlungLubrication / cooling
33
NiederdruckkreisLow pressure circuit
44
erste Hydropumpefirst hydraulic pump
55
zweite Hydropumpesecond hydraulic pump
66
erster Hauptdruckreglerfirst main pressure regulator
6.16.1
Kolbenpiston
6.26.2
erste Stirnseitefirst face
6.36.3
zweite Stirnseitesecond face
6.46.4
KolbenbetätigungsfederPiston actuator spring
6.56.5
öffnender Kolbenabschnittopening piston section
6.66.6
öffnender Kolbenabschnittopening piston section
6.76.7
schließender Kolbenabschnittclosing piston section
6.86.8
schließender Kolbenabschnittclosing piston section
6.96.9
schließender Kolbenabschnittclosing piston section
6.106.10
Schlitzslot
6.116.11
Schlitzslot
6.126.12
Schlitzslot
6.136.13
Schlitzslot
6.146.14
Schlitzslot
6.156.15
Schlitzslot
6.166.16
Schlitzslot
6.176.17
Schlitzslot
77
zweiter Hauptdruckreglersecond main pressure regulator
7.17.1
Kolbenpiston
7.27.2
erste Stirnseitefirst face
7.37.3
zweite Stirnseitesecond face
7.47.4
Kolbenbetätigungsfeder Piston actuator spring
7.57.5
öffnender Kolbenabschnittopening piston section
7.67.6
öffnender Kolbenabschnittopening piston section
7.77.7
öffnender Kolbenabschnittopening piston section
7.87.8
schließender Kolbenabschnittclosing piston section
7.97.9
schließender Kolbenabschnittclosing piston section
7.107.10
schließender Kolbenabschnittclosing piston section
7.117.11
schließender Kolbenabschnittclosing piston section
7.127.12
Schlitzslot
7.137.13
Schlitzslot
7.147.14
Schlitzslot
7.157.15
Schlitzslot
7.167.16
Schlitzslot
7.177.17
Schlitzslot
7.187.18
Schlitzslot
7.197.19
Schlitzslot
88th
ElektromagnetventilSolenoid valve
99
ÜberdruckventilPressure relief valve
1010
Filterfilter
1111
Filterfilter
1212
VersorgungskreispOWER sUPPLY
1313
ZwischendruckkreisBetween pressure circuit
1414
DurchflussblendeFlow orifice
1515
Kühlercooler
1616
HydraulikflüssigkeitsreservoirHydraulic fluid reservoir
P4 P 4
Druck der ersten Hydropumpe 4Pressure of the first hydraulic pump 4
P5 P 5
Druck der zweiten Hydropumpe 5Pressure of the second hydraulic pump 5
PA P A
Druck im Hochdruckkreis 2Pressure in the high pressure circuit 2
PA'P A '
Druck in der Versorgungsleitung 2' des Hochdruckkreises 2 hinter der Durchflussblende 14Pressure in the supply line 2 'of the high pressure circuit 2 behind the flow orifice 14
PL P L
Druck im Niederdruckkreis 3Pressure in the low pressure circuit 3
P13 P 13
Druck im Zwischendruckkreis 13Pressure in the intermediate pressure circuit 13

Claims (14)

Hydraulisches Steuer- und Regelsystem (1) mit einem von einer ersten Hydropumpe (4) mit Hydraulikflüssigkeit gespeisten Hochdruckkreis (2), dessen Hochdruckniveau (PA) von einem ersten Hauptdruckregler (6) regelbar ist und mit einem von einer zweiten Hydropumpe (5) mit Hydraulikflüssigkeit gespeisten Niederdruckkreis (3), dessen Niederdruckniveau (PL) von einem zweiten Hauptdruckregler (7) regelbar ist dadurch gekennzeichnet, dass in dem Hochdruckkreis (2) ein Hydraulikflüssigkeitsablass (6.14, 6.6, 6.15) vorgesehen ist, über den der Niederdruckkreis (3) mit überschüssiger Hydraulikflüssigkeit aus dem Hochdruckreis (2) speisbar ist und/oder dass in dem Hochdruckkreis (2) ein Hydraulikflüssigkeitseinlass (6.12, 6.5, 6.13) vorgesehen ist, über den der Hochdruckkreis (2) mit fehlender Hydraulikflüssigkeit von der zweiten Hydropumpe (5) speisbar ist. Hydraulic control system (1) with a high pressure circuit (2) fed with hydraulic fluid by a first hydraulic pump (4), the high pressure level (P A ) of which can be regulated by a first main pressure regulator (6) and with a low pressure circuit (3) fed with hydraulic fluid by a second hydraulic pump (5), the low pressure level (P L ) of which can be regulated by a second main pressure regulator (7) characterized in that A hydraulic fluid drain (6.14, 6.6, 6.15) is provided in the high pressure circuit (2), via which the low pressure circuit (3) can be fed with excess hydraulic fluid from the high pressure rice (2) and / or that A hydraulic fluid inlet (6.12, 6.5, 6.13) is provided in the high pressure circuit (2), via which the high pressure circuit (2) can be fed from the second hydraulic pump (5) with missing hydraulic fluid. Hydraulisches Steuer- und Regelsystem (1) nach Anspruch 1,
dadurch gekennzeichnet, dass
der Hydraulikflüssigkeitsablass (6.14, 6.5, 6.15) und/oder der Hydraulikflüssigkeitseinlass (6.12, 6.5, 6.13) Bestandteile des ersten Hauptdruckreglers (6) sind.Hydraulic control and regulating system (1) according to claim 1,
characterized in that
the hydraulic fluid drain (6.14, 6.5, 6.15) and / or the hydraulic fluid inlet (6.12, 6.5, 6.13) are components of the first main pressure regulator (6). Hydraulisches Steuer- und Regelsystem (1) nach Anspruch 1 oder 2,
dadurch gekennzeichnet, dass
in dem Hochdruckkreis (2) ein Ventil (8) vorgesehen ist, welcher den ersten Hauptdruckregler (6) in Abhängigkeit vom Druck (PA) im Hochdruckkreis (2) steuert.Hydraulic control and regulating system (1) according to claim 1 or 2,
characterized in that
A valve (8) is provided in the high pressure circuit (2) and controls the first main pressure regulator (6) as a function of the pressure (P A ) in the high pressure circuit (2). Hydraulisches Steuer- und Regelsystem (1) nach einem der vorangegangenen Ansprüche,
dadurch gekennzeichnet, dass
ein von der zweiten Hydropumpe (5) mit Hydraulikflüssigkeit gespeister Zwischendruckkreis (13) vorgesehen ist, über den der Niederdruckkreis (3) mit der Hydraulikflüssigkeit speisbar ist und/oder über den der Hochdruckkreis (2) mit der fehlenden Hydraulikflüssigkeit speisbar ist.Hydraulic control and regulating system (1) according to one of the preceding claims,
characterized in that
An intermediate pressure circuit (13) fed by the second hydraulic pump (5) with hydraulic fluid is provided, via which the low pressure circuit (3) can be fed with the hydraulic fluid and / or via which the high pressure circuit (2) can be fed with the missing hydraulic fluid. Hydraulisches Steuer- und Regelsystem (1) nach Anspruch 4,
dadurch gekennzeichnet, dass
die Speisung des Niederdruckkreises (3) mit der Hydraulikflüssigkeit aus dem Zwischendruckkreis (13) und/oder die Speisung des Hochdruckkreises (2) mit der fehlenden Hydraulikflüssigkeit aus dem Zwischendruckkreis (13) von dem ersten Hauptdruckregler (6) regelbar ist.Hydraulic control and regulating system (1) according to claim 4,
characterized in that
the supply of the low pressure circuit (3) with the hydraulic fluid from the intermediate pressure circuit (13) and / or the supply of the high pressure circuit (2) with the missing hydraulic fluid from the intermediate pressure circuit (13) can be regulated by the first main pressure regulator (6). Hydraulisches Steuer- und Regelsystem (1) nach Anspruch 5,
dadurch gekennzeichnet, dass
in dem Zwischendruckkreis (13) ein Überdruckventil (9) vorgesehen ist, über das der Niederdruckkreis (3) mit überschüssiger Hydraulikflüssigkeit aus dem Zwischendruckkreis (13) speisbar ist.Hydraulic control and regulating system (1) according to claim 5,
characterized in that
A pressure relief valve (9) is provided in the intermediate pressure circuit (13), via which the low pressure circuit (3) can be fed with excess hydraulic fluid from the intermediate pressure circuit (13). Verfahren zum Einstellen von hydraulischen Druckniveaus bei dem ein Hochdruckniveau (PA) in einem von einer ersten Hydropumpe (4) mit Hydraulikflüssigkeit gespeisten Hochdruckkreis (2) von einem ersten Hochdruckregler (6) geregelt wird und bei dem ein Niederdruckniveau (PL) in einem von einer zweiten Hydropumpe (5) mit Hydraulikflüssigkeit gespeisten Niederdruckkreis (3) von einem zweiten Hauptdruckregler (7) geregelt wird dadurch gekennzeichnet, dass der Niederdruckkreis (3) mit überschüssiger Hydraulikflüssigkeit aus dem Hochdruckkreis (2) gespeist wird und/oder dass der Hochdruckkreis (2) mit fehlender Hydraulikflüssigkeit von der zweiten Hydropumpe (5) gespeist wird. Procedure for adjusting hydraulic pressure levels at which a high pressure level (P A ) in a high pressure circuit (2) fed with hydraulic fluid by a first hydraulic pump (4) is regulated by a first high pressure regulator (6) and A low pressure level (P L ) in a low pressure circuit (3) supplied with hydraulic fluid by a second hydraulic pump (5) is regulated by a second main pressure regulator (7) characterized in that the low pressure circuit (3) is supplied with excess hydraulic fluid from the high pressure circuit (2) and / or that the high pressure circuit (2) is supplied with missing hydraulic fluid from the second hydraulic pump (5). Verfahren nach Anspruch 7,
dadurch gekennzeichnet, dass
die Speisung des Niederdruckkreises (3) mit der überschüssigen Hydraulikflüssigkeit aus dem Hochdruckkreis (2) und/oder die Speisung des Hochdruckkreises (2) mit der fehlenden Hydraulikflüssigkeit von der zweiten Hydropumpe (5) von dem ersten Hauptdruckregler (6) geregelt wird.Method according to claim 7,
characterized in that
the supply of the low pressure circuit (3) with the excess hydraulic fluid from the high pressure circuit (2) and / or the supply of the high pressure circuit (2) with the missing hydraulic fluid from the second hydraulic pump (5) is regulated by the first main pressure regulator (6). Verfahren nach Anspruch 8,
dadurch gekennzeichnet, dass
der erste Hauptdruckregler (6) von einem in dem Hochdruckkreis (2) vorgesehenen Ventil (8) in Abhängigkeit von dem Druck (PA) in Hochdruckkreis (2) gesteuert wird.A method according to claim 8,
characterized in that
the first main pressure regulator (6) is controlled by a valve (8) provided in the high pressure circuit (2) as a function of the pressure (P A ) in the high pressure circuit (2). Verfahren nach einem der Ansprüche 7 bis 9,
dadurch gekennzeichnet, dass
von der zweiten Hydropumpe (5) ein Zwischendruckkreis (13) mit Hydraulikflüssigkeit gespeist wird, über den der Niederdruckkreis (3) mit der Hydraulikflüssigkeit gespeist wird und/oder über den der Hochdruckkreis (2) mit der fehlenden Hydraulikflüssigkeit gespeist wird. Method according to one of claims 7 to 9,
characterized in that
from the second hydraulic pump (5) an intermediate pressure circuit (13) is supplied with hydraulic fluid, via which the low pressure circuit (3) is supplied with the hydraulic fluid and / or via which the high pressure circuit (2) is supplied with the missing hydraulic fluid. Verfahren nach Anspruch 10,
dadurch gekennzeichnet, dass
die Speisung des Niederdruckkreises (3) mit der Hydraulikflüssigkeit aus dem Zwischendruckkreis (13) und/oder die Speisung des Hochdruckkreises (2) mit der fehlenden Hydraulikflüssigkeit aus dem Zwischendruckkreis (13) von dem ersten Hauptdruckregler (6) geregelt wird.A method according to claim 10,
characterized in that
the supply of the low pressure circuit (3) with the hydraulic fluid from the intermediate pressure circuit (13) and / or the supply of the high pressure circuit (2) with the missing hydraulic fluid from the intermediate pressure circuit (13) is regulated by the first main pressure regulator (6). Verfahren nach Anspruch 11,
dadurch gekennzeichnet, dass
der Niederdruckkreis (3) bei Überdruck in dem Zwischendruckkreis (13) über ein Überdruckventil (9) mit der überschüssigen Hydraulikflüssigkeit aus dem Zwischendruckkreis (13) gespeist wird.A method according to claim 11,
characterized in that
the low-pressure circuit (3) is supplied with the excess hydraulic fluid from the intermediate pressure circuit (13) via an overpressure valve (9) in the event of excess pressure in the intermediate pressure circuit (13). Verwendung des Verfahrens nach einem der Ansprüche 7 bis 12 zur Druckregelung in einem Automatikgetriebe, insbesondere in einem Doppelkupplungsgetriebe.Use of the method according to one of claims 7 to 12 for pressure control in an automatic transmission, in particular in a double clutch transmission. Automatikgetriebe, insbesondere Doppelkupplungsgetriebe, mit einem hydraulischen Steuer- und Regelsystem (1) nach einem der Ansprüche 1 bis 6.Automatic transmission, in particular double clutch transmission, with a hydraulic control and regulation system (1) one of claims 1 to 6.
EP03008967A 2003-04-17 2003-04-17 Hydraulic control and regulating system and method for adjusting the hydraulic pressure levels Withdrawn EP1469235A1 (en)

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EP1722121A1 (en) * 2005-05-09 2006-11-15 HOERBIGER Antriebstechnik GmbH Hydraulic double clutch
DE102008000679A1 (en) * 2008-03-14 2009-09-17 Zf Friedrichshafen Ag Hydraulic control arrangement for controlling a variable fluid volume flow
DE102008040269A1 (en) * 2008-07-09 2010-02-18 Zf Friedrichshafen Ag Method for recognition of malfunctioning of pressure relief valve integrated into secondary cycle for transmission radiator in double coupling transmission, involves determining pressure indirectly by coupling pressure sensor
US8192176B2 (en) 2009-12-10 2012-06-05 GM Global Technology Operations LLC Hydraulic fluid supply system having active regulator
US8225687B2 (en) 2009-09-09 2012-07-24 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8403793B2 (en) 2010-02-17 2013-03-26 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a lubrication regulation valve
US8403792B2 (en) 2009-10-21 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8402855B2 (en) 2010-01-11 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8413777B2 (en) 2010-02-17 2013-04-09 GM Global Technology Operations LLC High efficiency hydraulic transmission control system
US8413437B2 (en) 2009-12-08 2013-04-09 GM Global Technology Operations LLC Transmission hydraulic control system having independently controlled stator cooling flow
US8429994B2 (en) 2009-09-09 2013-04-30 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8435148B2 (en) 2010-01-11 2013-05-07 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having electronic transmission range selection with failure mode control
US8443687B2 (en) 2009-12-14 2013-05-21 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US8475336B2 (en) 2009-07-30 2013-07-02 GM Global Technology Operations LLC Hydraulic control system for a dual clutch transmission
US8500600B2 (en) 2011-01-10 2013-08-06 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a manual valve with a two gear default strategy
US8567580B2 (en) 2010-01-22 2013-10-29 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US8579094B2 (en) 2010-01-11 2013-11-12 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a three path torque converter control subsystem
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US8733521B2 (en) 2010-12-06 2014-05-27 Gm Global Technology Operations Apparatus for and method of controlling a dual clutch transmission
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CN101774378B (en) * 2008-09-25 2014-06-25 通用汽车环球科技运作公司 Auxiliary pump system for hybrid powertrains
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US8915076B2 (en) 2011-01-12 2014-12-23 Gm Global Technology Operations, Llc Transmission hydraulic control system having flow augmentation
US8942901B2 (en) 2010-12-09 2015-01-27 Gm Global Technology Operations, Llc Method of controlling a hydraulic control system for a dual clutch transmission
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US10167948B2 (en) 2016-03-17 2019-01-01 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission
DE102018214430A1 (en) * 2018-08-27 2020-02-27 Zf Friedrichshafen Ag Hydraulic system for a double clutch transmission
DE102018214433A1 (en) * 2018-08-27 2020-02-27 Zf Friedrichshafen Ag Hydraulic system for a transmission of a motor vehicle drive train
DE102018218123A1 (en) * 2018-10-23 2020-04-23 Zf Friedrichshafen Ag Cooling valve for a hydraulic system of a motor vehicle transmission
DE102019201709A1 (en) * 2019-02-11 2020-08-13 Volkswagen Aktiengesellschaft Oil system, in particular oil system for a motor vehicle, with a valve for filling a high-pressure branch reservoir from a low-pressure branch
DE102011051426B4 (en) 2010-12-03 2021-08-05 Hyundai Motor Co. Hydraulic pump system of an automatic transmission
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EP1722121A1 (en) * 2005-05-09 2006-11-15 HOERBIGER Antriebstechnik GmbH Hydraulic double clutch
WO2006119973A1 (en) * 2005-05-09 2006-11-16 Hoerbiger Antriebstechnik Gmbh Hydraulic double clutch
DE102008000679A1 (en) * 2008-03-14 2009-09-17 Zf Friedrichshafen Ag Hydraulic control arrangement for controlling a variable fluid volume flow
US8464755B2 (en) 2008-03-14 2013-06-18 Zf Friedrichshafen Ag Hydraulic control arrangement for controlling a variable fluid volume flow
DE102008040269A1 (en) * 2008-07-09 2010-02-18 Zf Friedrichshafen Ag Method for recognition of malfunctioning of pressure relief valve integrated into secondary cycle for transmission radiator in double coupling transmission, involves determining pressure indirectly by coupling pressure sensor
CN101774378B (en) * 2008-09-25 2014-06-25 通用汽车环球科技运作公司 Auxiliary pump system for hybrid powertrains
US8475336B2 (en) 2009-07-30 2013-07-02 GM Global Technology Operations LLC Hydraulic control system for a dual clutch transmission
US8225687B2 (en) 2009-09-09 2012-07-24 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8429994B2 (en) 2009-09-09 2013-04-30 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8403792B2 (en) 2009-10-21 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8413437B2 (en) 2009-12-08 2013-04-09 GM Global Technology Operations LLC Transmission hydraulic control system having independently controlled stator cooling flow
US8192176B2 (en) 2009-12-10 2012-06-05 GM Global Technology Operations LLC Hydraulic fluid supply system having active regulator
US8443687B2 (en) 2009-12-14 2013-05-21 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US8402855B2 (en) 2010-01-11 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8435148B2 (en) 2010-01-11 2013-05-07 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having electronic transmission range selection with failure mode control
US8579094B2 (en) 2010-01-11 2013-11-12 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a three path torque converter control subsystem
US8567580B2 (en) 2010-01-22 2013-10-29 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US8413777B2 (en) 2010-02-17 2013-04-09 GM Global Technology Operations LLC High efficiency hydraulic transmission control system
US8403793B2 (en) 2010-02-17 2013-03-26 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a lubrication regulation valve
US8839928B2 (en) 2010-12-02 2014-09-23 Gm Global Technology Operations, Llc Electro-hydraulic control system for a dual clutch transmission
DE102011051426B4 (en) 2010-12-03 2021-08-05 Hyundai Motor Co. Hydraulic pump system of an automatic transmission
US8733521B2 (en) 2010-12-06 2014-05-27 Gm Global Technology Operations Apparatus for and method of controlling a dual clutch transmission
US8904893B2 (en) 2010-12-06 2014-12-09 Gm Global Technology Operations, Llc Method of controlling a dual clutch transmission
US8738257B2 (en) 2010-12-08 2014-05-27 Gm Global Technology Operations, Llc Electro-hydraulic control system and method for a dual clutch transmission
US8740748B2 (en) 2010-12-08 2014-06-03 Gm Global Technology Operations, Llc Control system and method for a dual clutch transmission
US9765885B2 (en) 2010-12-09 2017-09-19 GM Global Technology Operations LLC Method of controlling a hydraulic control system for a dual clutch transmission
US8942901B2 (en) 2010-12-09 2015-01-27 Gm Global Technology Operations, Llc Method of controlling a hydraulic control system for a dual clutch transmission
US8500600B2 (en) 2011-01-10 2013-08-06 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a manual valve with a two gear default strategy
US8915076B2 (en) 2011-01-12 2014-12-23 Gm Global Technology Operations, Llc Transmission hydraulic control system having flow augmentation
US8702548B2 (en) 2011-11-03 2014-04-22 Gm Global Technology Operations Hydraulic control system for an automatic transmission
US9080666B2 (en) 2012-05-29 2015-07-14 Gm Global Technology Operations, Inc. Discrete mechanism for electronic transmission range selection
DE102015205199A1 (en) * 2015-03-23 2016-09-29 Zf Friedrichshafen Ag Apparatus and method for ensuring the oil supply of the secondary circuit of a hydraulic circuit of a multi-stage automatic transmission of a motor vehicle, comprising a main input side driven oil pump and an electrically driven, fluidly connected to the primary circuit of the hydraulic circuit auxiliary oil pump
US10167948B2 (en) 2016-03-17 2019-01-01 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission
DE102018214430A1 (en) * 2018-08-27 2020-02-27 Zf Friedrichshafen Ag Hydraulic system for a double clutch transmission
DE102018214433A1 (en) * 2018-08-27 2020-02-27 Zf Friedrichshafen Ag Hydraulic system for a transmission of a motor vehicle drive train
DE102018218123A1 (en) * 2018-10-23 2020-04-23 Zf Friedrichshafen Ag Cooling valve for a hydraulic system of a motor vehicle transmission
DE102019201709A1 (en) * 2019-02-11 2020-08-13 Volkswagen Aktiengesellschaft Oil system, in particular oil system for a motor vehicle, with a valve for filling a high-pressure branch reservoir from a low-pressure branch
DE102020104504A1 (en) 2020-02-20 2021-08-26 Fte Automotive Gmbh Assembly for actuating a clutch in the drive train of a motor vehicle

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